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WO2011078547A2 - Compresseur à capacité variable - Google Patents

Compresseur à capacité variable Download PDF

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Publication number
WO2011078547A2
WO2011078547A2 PCT/KR2010/009147 KR2010009147W WO2011078547A2 WO 2011078547 A2 WO2011078547 A2 WO 2011078547A2 KR 2010009147 W KR2010009147 W KR 2010009147W WO 2011078547 A2 WO2011078547 A2 WO 2011078547A2
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
discharge
valve body
chamber
refrigerant inlet
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/KR2010/009147
Other languages
English (en)
Korean (ko)
Other versions
WO2011078547A3 (fr
Inventor
이건호
김기범
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Doowon Electronics Co Ltd
Doowon Technical College
Original Assignee
Doowon Electronics Co Ltd
Doowon Technical College
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from KR1020090129438A external-priority patent/KR101601966B1/ko
Priority claimed from KR1020090129441A external-priority patent/KR20110072490A/ko
Application filed by Doowon Electronics Co Ltd, Doowon Technical College filed Critical Doowon Electronics Co Ltd
Publication of WO2011078547A2 publication Critical patent/WO2011078547A2/fr
Publication of WO2011078547A3 publication Critical patent/WO2011078547A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/025—Check valves with guided rigid valve members the valve being loaded by a spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/06—Check valves with guided rigid valve members with guided stems
    • F16K15/063—Check valves with guided rigid valve members with guided stems the valve being loaded by a spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0413—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded in the form of closure plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1809—Controlled pressure
    • F04B2027/1818—Suction pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/185—Discharge pressure

Definitions

  • the present invention relates to a variable displacement compressor, and more particularly, to a variable displacement compressor that minimizes the difference between the inlet side discharge pressure and the outlet side discharge pressure of the check valve.
  • variable capacity compressor that can change the discharge amount of the refrigerant to obtain a cooling capacity without being regulated by the rotational speed of the engine has been used a lot.
  • variable displacement compressors such as swash plate type, rotary type and scroll type.
  • the swash plate type compressor In the swash plate type compressor, the swash plate provided so that the inclination angle is variable in the crank chamber rotates according to the rotational motion of the rotating shaft, and the piston reciprocates by the rotational motion of the swash plate.
  • the refrigerant in the suction chamber is sucked into the cylinder by the reciprocating motion of the piston, compressed and discharged into the discharge chamber.
  • the inclination angle of the swash plate is changed according to the pressure difference in the crank chamber and the pressure in the suction chamber, and the discharge amount of the refrigerant is changed. Will be controlled.
  • the operation of the capacity control valve is calculated by a control unit in which a signal such as the detected engine speed, the temperature inside or outside the vehicle, the evaporator temperature, or the like is incorporated by the CPU, and based on the result of the calculation, the current By sending it to an electromagnetic coil.
  • a check valve is provided at the discharge port communicating with the discharge chamber to prevent the leakage of the refrigerant during the minimum capacity operation of the compressor.
  • FIG. 1 is a longitudinal sectional view showing a check valve of a variable displacement compressor according to the prior art.
  • the check valve 1 includes a valve housing 2 in which a refrigerant inlet 2a through which discharged refrigerant is introduced and a refrigerant outlet 2b through which discharged refrigerant is discharged are respectively formed. And a valve body 3 for reciprocating the inside of the valve housing 2 to open and close the refrigerant inlet 2a and the refrigerant outlet 2b, and a cover 4 covering the open end of the valve housing 2. And a spring 5 interposed between the cover 4 and the valve body 3.
  • the check valve 1 configured as described above is installed at the discharge port of the compressor to prevent leakage of the refrigerant during the minimum capacity operation (at low pressure discharge).
  • the inlet discharge pressure PdH flowing into the first refrigerant inlet 2a pressurizes the upper portion of the valve body 3 and simultaneously compresses the spring 5 so that the pressure is lowered.
  • the pressure PdL is sent to the next cooling cycle through the refrigerant outlet 2b.
  • the output discharge pressure PdL discharged to the refrigerant discharge port 2b is lower than the inlet discharge pressure PdH flowing into the first refrigerant inlet 2a.
  • the present invention has been made to solve the above-mentioned general problems, and an object of the present invention is to provide a check valve with an inlet discharge pressure of a check valve by actuating a crankcase or a suction chamber pressure that increases or decreases in a direction opposite to the discharge chamber pressure. It is to provide a variable displacement compressor that minimizes the difference between the discharge pressure of the outlet and the outlet.
  • Another object of the present invention is to provide a variable displacement compressor configured to close the check valve by the pressure of the reverse flow refrigerant discharged during the minimum inclination angle of the swash plate to prevent the reverse flow of the discharge refrigerant.
  • a variable displacement compressor including: a discharge flow passage connected to the discharge chamber, the displacement variable compressor having a suction chamber, a discharge chamber, and a crank chamber; And a check valve mounted in the discharge passage to open and close the discharge passage by a differential pressure between the discharge chamber pressure and the crank chamber or suction chamber pressure.
  • the check valve may further include a valve housing having a first refrigerant inlet through which the discharge chamber pressure acts and a refrigerant outlet connected to the first refrigerant inlet, and having an end portion opposite to the first refrigerant inlet; A valve body for opening and closing the first refrigerant inlet; A cover having a second refrigerant inlet through which the crank chamber or suction chamber pressure is applied and covering the open end of the valve housing; And a biasing member interposed between the cover and the valve body.
  • the valve body is composed of a large diameter portion corresponding to the first refrigerant inlet and a small diameter portion corresponding to the second refrigerant inlet.
  • an elastic member is interposed between the large diameter portion and the small diameter portion.
  • the large diameter portion is preferably formed with a seating groove in which the elastic member is seated.
  • the check valve preferably opens the discharge passage when the discharge chamber pressure is larger than the elastic force of the biasing member plus the pressure of the crank chamber or the suction chamber.
  • valve body is preferably composed of a first valve body for opening and closing the first refrigerant inlet and a second valve body corresponding to the second refrigerant inlet.
  • the first valve body is formed with a hydraulic pressure portion to which the discharged backflow refrigerant acts, and the second valve body has a support portion inserted into the hydraulic pressure portion.
  • the hydraulic portion is preferably formed with a guide portion is inserted into the support portion to hold the initial position.
  • the guide portion is preferably an inclined portion that narrows in the insertion direction.
  • the biasing member is seated on the radially outer side of the guide part.
  • crank chamber or the suction chamber is preferably provided with a connection passage for connecting the check valve.
  • variable displacement compressor According to the variable displacement compressor according to the present invention, the difference between the inlet side discharge pressure and the outlet side discharge pressure of the check valve is minimized by acting on the small diameter portion of the valve body to increase or decrease the crankcase or suction chamber pressure in a direction opposite to the discharge chamber pressure. It is effective.
  • the first valve body when the reverse flow refrigerant discharged from the hydraulic portion of the first valve body acts during the minimum inclination angle driving of the swash plate, the first valve body has an effect of preventing the reverse flow of the discharge refrigerant by closing the first refrigerant inlet.
  • FIG. 1 is a longitudinal sectional view showing a check valve of a variable displacement compressor according to the prior art.
  • FIG. 2 is a longitudinal sectional view showing the structure of a variable displacement compressor according to the present invention.
  • FIG. 3 is a side cross-sectional view illustrating a rear housing of the variable displacement compressor of FIG. 2.
  • FIG. 4 is a longitudinal sectional view showing a structure of a check valve according to a first embodiment of the present invention.
  • FIG. 5 is a longitudinal sectional view showing a structure of a check valve according to a second embodiment of the present invention.
  • variable displacement swash plate compressor provided with a valve assembly according to the present invention
  • Figure 2 is a longitudinal sectional view showing a structure of a variable displacement compressor according to the present invention
  • Figure 3 is a side cross-sectional view showing a rear housing of the variable displacement compressor of Figure 2
  • Figure 4 is a check according to a first embodiment of the present invention
  • 5 is a longitudinal sectional view showing the structure of a valve
  • FIG. 5 is a longitudinal sectional view showing the structure of a check valve according to a second embodiment of the present invention.
  • variable displacement swash plate type compressor C has a cylinder block 10 having a plurality of cylinder bores 12 formed parallel to the inner circumferential surface in the longitudinal direction, and sealed in front of the cylinder block 10.
  • the front housing 16 is coupled, and the rear housing 18 is hermetically coupled via a valve plate 20 at the rear of the cylinder block 10.
  • the crank chamber 86 is provided inside the front housing 16, and one end of the drive shaft 44 is rotatably supported near the center of the front housing 16, while the other end of the drive shaft 44 is Passed through the crank chamber 86 is supported via a bearing provided in the cylinder block 10.
  • the lug plate 54 and the swash plate 50 are provided around the drive shaft 44.
  • a pair of power transmission support arms 62 each having a linearly perforated guide hole 64 formed at the center thereof are formed to protrude integrally on one surface, and one surface of the swash plate 50 has a ball.
  • the ball 66 of the swash plate 50 slides in the guide hole 64 of the lug plate 54 so that the swash plate 50 can be rotated.
  • the inclination angle is variable.
  • the outer circumferential surface of the swash plate 50 is fitted to the piston 14 so as to be able to slide through the shoe 76.
  • a suction chamber 22 and a discharge chamber 24 are formed in the rear housing 18, and each cylinder bore is provided in the valve plate 20 interposed between the rear housing 18 and the cylinder block 10.
  • the intake valve 32 and the discharge valve 36 are formed in the place corresponding to (12), respectively.
  • the refrigerant in the suction chamber 22 is sucked into the cylinder bore 12, compressed, and discharged to the discharge chamber 24.
  • the pressure in the crank chamber 86 and the suction chamber ( 22) or the inclination angle of the swash plate 50 is changed in accordance with the pressure difference in the discharge chamber 24 to adjust the discharge amount of the refrigerant, which adjusts the pressure of the crank chamber 86 by opening and closing the valve by energization. It is usually implemented by the capacity control valve 200 to adjust the inclination angle of the swash plate 50 to adjust the discharge capacity.
  • a discharge flow path 101 communicating with the discharge chamber 24 is formed in the rear housing 18.
  • the discharge passage 101 is provided with a check valve 100 for discharging the refrigerant compressed at a predetermined differential pressure or more to an external cooling cycle (condenser) and at the same time to prevent the reverse flow of the discharged refrigerant.
  • the discharge port 25 is preferably formed on the discharge side of the discharge passage 101.
  • the rear housing 18 is formed with a connection passage 102 for connecting the pressures Pc and PS of the crank chamber 86 or the suction chamber 22 to act on the check valve 100.
  • the compressor described above is just one example in which the check valve according to the present invention is installed, and is applicable to all other clutch-less displacement variable compressors.
  • the check valve 100 according to the first embodiment of the present invention is mounted in the discharge passage 101, the discharge chamber 24 pressure (Pd) and the crank chamber 86 Alternatively, the check valve 100 according to the present invention, which opens and closes the discharge flow path 101 by the differential pressures of the pressures Pc and Ps of the suction chamber 22, performs the next cooling cycle on the refrigerant discharged from the discharge chamber 24.
  • the valve housing 110, the valve body 120 for reciprocating the inside of the valve housing 110, and the open of the valve housing 120 A cover 130 covering an end portion and a biasing member 140 interposed between the cover 130 and the valve body 120 are included.
  • valve housing 110 is connected to the first refrigerant inlet 111 according to the reciprocating movement of the first refrigerant inlet 111 and the valve body 120 in which the discharge chamber 24 pressure Pd is applied.
  • the refrigerant outlet 112 is formed.
  • the first refrigerant inlet 111 is connected to the discharge chamber 24 by the discharge passage 101
  • the first refrigerant outlet 112 is connected to the discharge outlet 25 by the discharge passage 101.
  • the valve housing 110 is installed in the discharge passage 101.
  • valve body 120 opens and closes the aforementioned first refrigerant inlet 111 by the pressure Pd of the discharge chamber 24.
  • the cover 130 is formed with a second refrigerant inlet 131 in which the crank chamber 86 or the suction chamber 22 pressures Pc and Ps act.
  • the second refrigerant inlet 131 is connected to the connection passage 102.
  • the biasing member 140 is formed of a spring to apply an elastic force in the direction in which the valve body 120 closes the first refrigerant inlet 111.
  • the biasing member 140 may adjust the pressure difference of opening and closing the valve body 120 according to the size of the elastic modulus.
  • valve body 120 corresponds to the first refrigerant inlet 111 and corresponds to the large diameter portion 121 and the second refrigerant inlet 131 on which the discharge chamber 24 pressure Pd acts, and the crank chamber. 86 or a small diameter portion 122 in which the suction chamber 22 pressures Pc and Ps act.
  • the size of the discharge chamber 24 pressure Pd is equal to the elastic force of the biasing member 140 and the pressure Pc of the crank chamber 86 or the suction chamber 22.
  • the discharge passage 101 is opened.
  • the discharge chamber 24 pressure Pd is 100 or more.
  • the check valve 100 is to open the discharge flow path 101.
  • the pressure Pc and Ps of the crank chamber 86 or the suction chamber 22 is equal to the sum of the elastic force of the biasing member 140 and the pressures Pc and Ps of the crank chamber 86 or the suction chamber 22.
  • the difference between the inlet-side discharge pressure PdH and the outlet-side discharge pressure PdL of the check valve 100 may be further reduced.
  • the discharge chamber 24 pressure Pd is actually the biasing member ( If only the force of the elastic force of 10 or more of the 140 is consumed, the check valve 100 is opened. That is, the pressures Pc and Ps of the crank chamber 86 or the suction chamber 22 increase or decrease in a direction opposite to the pressure Pd of the discharge chamber 24, so that the pressure of the crank chamber 86 or the suction chamber 22 is increased. (Pc, Ps) 90 is canceled by the pressure Pd of the discharge chamber 24.
  • crank chamber 86 or the suction chamber pressure Pc acts on the small diameter portion 122 of the valve body 120 even when the elastic force decreases as the compression and swelling of the biasing member 140 are repeated. You can also completely block backflow.
  • FIG. 4 shows that the valve body 120 compresses the biasing member 140 by the discharge chamber 24 pressure Pd, and then cools the compressed refrigerant by opening the first refrigerant inlet 111. 4 (b) is driven at the minimum inclination angle of the swash plate 50 so that the elastic force and the crank chamber 86 pressure Pc of the biasing member 140 are applied to the valve body 120.
  • the valve body 120 acts to close the first refrigerant inlet 111 to prevent backflow of the refrigerant.
  • the large diameter portion 121 and the small diameter portion 122 is interposed between the elastic member 150, the large diameter portion 121 is formed with a seating groove 151 for mounting the elastic member 150.
  • the discharge passage 101 is mounted in the discharge passageway 101, and the pressure Pd of the discharge chamber 24 and the crank chamber 86 or the suction chamber 22 pressures Pc and Ps.
  • the check valve 100 which opens and closes the discharge passage 101 by differential pressure, repeatedly performs a function of sending the refrigerant discharged from the discharge chamber 24 to the next cooling cycle (condenser).
  • the valve housing 110 has a refrigerant connected to the refrigerant inlet 111 according to the reciprocating movement of the first refrigerant inlet 111 and the valve body 120 in which the discharge chamber 24 pressure Pd is applied.
  • An outlet 112 is formed.
  • the first refrigerant inlet 111 is connected to the discharge chamber 24 by the discharge passage 101, and the refrigerant outlet 112 is connected to the discharge outlet 25 by the discharge passage 101. That is, the valve housing 110 is installed in the discharge passage 101.
  • valve body 120 opens and closes the aforementioned first refrigerant inlet 111 by the pressure Pd of the discharge chamber 24.
  • valve body 120 has a reverse flow refrigerant discharged during the driving of the minimum inclination angle of the compressor, which will be described later.
  • the cover 130 is formed with a second refrigerant inlet 131 in which the crank chamber 86 or the suction chamber pressures Pc and Ps act. That is, the second refrigerant inlet 131 is connected to the connection passage 102.
  • the biasing member 140 is formed of a spring to apply an elastic force in the direction in which the valve body 120 closes the first refrigerant inlet 111.
  • the biasing member 140 may adjust the pressure difference of opening and closing the valve body 120 according to the size of the elastic modulus.
  • valve body 120 includes a first valve body 121 that opens and closes the first refrigerant inlet 111, and a second valve body 122 corresponding to the second refrigerant inlet 112.
  • the first and second valve bodies 121 and 122 are separately configured to move, respectively.
  • the biasing member 140 preferably applies an elastic force to the first valve body 121.
  • first valve body 121 is formed with a pressure receiving portion 121a to which discharged backflow refrigerant acts, and the second valve body 122 has a support portion 122a inserted into the hydraulic pressure portion 121a. A) is formed.
  • the hydraulic pressure portion 121a is formed with a guide portion 150 into which the support portion 122a is inserted to hold an initial position, and the guide portion 150 is preferably an inclined portion that narrows in the insertion direction.
  • biasing member 140 is seated on the radially outer side of the guide part 150.
  • the check valve 100 of the present invention prevents the reverse flow of the discharged refrigerant even when the differential pressure is increased as shown in Table 1 below when the reverse flow refrigerant discharged to the hydraulic unit 121a operates. Done.
  • the first valve body 121 by the reverse flow refrigerant discharged to the hydraulic pressure portion 121a of the first valve body 121 when the swash plate 50 is driven at the minimum inclination angle. ) Closes the first refrigerant inlet 111 to prevent backflow of the discharged refrigerant.
  • the elastic force of the biasing member 140 also acts on the first valve body 121.
  • the differential pressure is higher than the above-described [Table 1] and the set pressure by the action of the reverse flow refrigerant discharged to the second valve body 122 and the first valve body 121 and the hydraulic pressure unit 121a reciprocating respectively. In this case, the reverse flow of the discharged refrigerant is completely blocked.
  • the crank chamber 86 or the suction chamber 22 pressures Pc and Ps are transmitted to the second refrigerant inlet 131 to act on the lower portion of the second valve body 122.
  • the second valve body 122 which receives the pressure Pc and Ps of the suction chamber 22, rises, and the support part 122a supports the lower part of the hydraulic pressure part 121a so that the first refrigerant inlet 111 ) Will remain closed.
  • the pressure Pc, Ps of the crank chamber 86 or the suction chamber 22 rises at the time of driving the minimum inclination angle of the swash plate 50, and the pressure Cc of the raised crank chamber 86 or the suction chamber 22 is increased. Ps) is to act on the check valve 100 through the connection flow path (102). At this time, in use of the compressor, the crankcase pressure Pc and the suction chamber pressure Ps become approximately equal.
  • the valve body 120 compresses the biasing member 140 by the pressure Pd of the discharge chamber 24 and then cools the compressed refrigerant by opening the first refrigerant inlet 111.
  • the discharge (FULL OPEN) to the cycle (condenser), Figure 5 (b) is the reverse flow refrigerant discharged to the water pressure portion 121a of the first valve sleeve 121 when driven at the minimum inclination angle of the swash plate 50 It acts to raise only the first valve body 121 to close the first refrigerant inlet 111 (BACK FLOW CLOSE) to prevent the backflow of the refrigerant.
  • BACK FLOW CLOSE the first refrigerant inlet 111
  • the crank chamber 86 or the suction chamber 22 pressures Pc and Ps act on the second valve body 122 so that the support part 122a of the second valve body 122 becomes the first.
  • the pressure receiving portion 121a of the valve body 121 By supporting the pressure receiving portion 121a of the valve body 121 to close the first refrigerant inlet 111 to prevent the backflow of the refrigerant.
  • the check valve 100 it is not necessary to limit the installation position of the check valve 100 as described above, and the check valve 100 if the discharge chamber 24 pressure Pd and the crank chamber 86 pressure Pc can act. Note that the installation location of the can be changed in various ways.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

La présente invention concerne un compresseur à capacité variable. Le compresseur à capacité variable comporte : un joint d'étanchéité d'admission, un joint d'étanchéité de manivelle et un joint d'étanchéité de refoulement ; une sortie de refoulement reliée audit joint d'étanchéité de refoulement et montée sur un passage de refoulement, et un clapet anti-retour qui ouvre et ferme le passage de refoulement sur la base des différentiels de pression dans le joint d'étanchéité d'admission, le joint d'étanchéité de manivelle et le joint d'étanchéité de refoulement. Par conséquent, le différentiel entre les pressions d'admission et de sortie du clapet anti-retour et la pression de refoulement à la sortie est réduit à un minimum par le fait de permettre aux pressions des joints d'étanchéité d'admission et de manivelle d'agir sur le côté éloigné du corps de clapet de telle sorte que la pression dans la direction opposée au joint d'étanchéité de refoulement est réduite.
PCT/KR2010/009147 2009-12-23 2010-12-21 Compresseur à capacité variable Ceased WO2011078547A2 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR10-2009-0129438 2009-12-23
KR10-2009-0129441 2009-12-23
KR1020090129438A KR101601966B1 (ko) 2009-12-23 2009-12-23 용량가변형 압축기
KR1020090129441A KR20110072490A (ko) 2009-12-23 2009-12-23 용량가변형 압축기

Publications (2)

Publication Number Publication Date
WO2011078547A2 true WO2011078547A2 (fr) 2011-06-30
WO2011078547A3 WO2011078547A3 (fr) 2011-11-10

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2010/009147 Ceased WO2011078547A2 (fr) 2009-12-23 2010-12-21 Compresseur à capacité variable

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WO (1) WO2011078547A2 (fr)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06185645A (ja) * 1992-12-18 1994-07-08 Toyoda Gosei Co Ltd 逆止弁
JP2002013474A (ja) * 2000-06-28 2002-01-18 Toyota Industries Corp 可変容量圧縮機
JP2005337044A (ja) * 2004-05-25 2005-12-08 Sanden Corp 可変容量斜板式圧縮機の機械式容量制御弁
KR101205221B1 (ko) * 2006-05-01 2012-11-27 한라공조주식회사 가변용량형 사판식 압축기

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